US10428826B2 - Method and system to reduce to wear on a bearing - Google Patents

Method and system to reduce to wear on a bearing Download PDF

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Publication number
US10428826B2
US10428826B2 US13/688,343 US201213688343A US10428826B2 US 10428826 B2 US10428826 B2 US 10428826B2 US 201213688343 A US201213688343 A US 201213688343A US 10428826 B2 US10428826 B2 US 10428826B2
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bearing
overpressure
compressor
turbine
shaft
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US13/688,343
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US20130142671A1 (en
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Matthias Stein
Thomas Steidten
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • F04D25/062—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic

Definitions

  • the present invention relates to a motor vehicle system device having a drive assembly to which a charging device is assigned which has a compressor having at least one compressor runner supported using at least one bearing, the bearing having a stationary first bearing part and a second bearing part that is operatively connected to the compressor runner.
  • the present invention further relates to a method for operating a motor vehicle system device.
  • Motor vehicle system devices of the type named at the outset are known from the related art. In principle, they have any desired devices with respect to systems of the motor vehicle, particularly, the drive assembly.
  • the charging device is supposed to be assigned to the drive assembly. It is used for the performance increase of the drive assembly, the drive assembly being able to be, for instance, an internal combustion engine or a fuel cell drive assembly having at least one fuel cell.
  • the charging device has the compressor, which is provided for compressing fluid, particularly gas, and air, for example. The fluid compressed using the charging device is usually supplied to the drive assembly. In this way, the specific power of the drive assembly is able to be clearly increased.
  • the compressor has a compressor runner, which is supported using the bearing, particularly in a housing, or rather, a compressor housing.
  • the bearing is made up of two bearing parts, namely, the first bearing part and the second bearing part.
  • the first bearing part is usually stationary, that is, it does not rotate, while the second bearing part is assigned to the compressor runner, or rather is connected to it in a torsionally rigid manner, that is, to rotate at the same rotational speed.
  • the second bearing part is present as a bearing bush and the second bearing part is present as a shaft area of a shaft, on which the compressor runner is situated in a manner resistant to torsion.
  • the charging device or rather the compressor, is usually actuated as a function of an operating state of the drive assembly, the compressor runner, and correspondingly the second bearing part being able to have changing rotational speeds with respect to the first bearing part.
  • the compressor runner may reach very high rotational speeds, in this context, particularly greater than 100,000 r.p.m. This sets very high requirements on the bearing which, for example, is developed as a sliding bearing. In motor vehicle system devices known from the related art, the bearing may be submitted to great wear.
  • the motor vehicle system device has the advantage that the wear of the bearing is able to be clearly reduced using a small effort.
  • this is achieved in that the bearing is connected to an overpressure source, using which an overpressure is able to be produced in a bearing gap present between the first bearing part and the second bearing part, the overpressure source being the compressor and/or a part of a tandem pump which, besides the overpressure, also provides a low air pressure for a user provided in the motor vehicle.
  • the bearing made up of a first bearing part and the second bearing part, may be designed as a fluid-dynamic, that is, a hydrodynamic or aerodynamic sliding bearing.
  • the bearing in the bearing, a so-called fluid bearing or air bearing is to be achieved, particularly at higher rotational speeds of the compressor runner, between the first and the second bearing part.
  • the bearing is developed as an air bearing, in which, during operation, preferably in at least a few operating regions, only fluid friction, particularly air friction takes place.
  • the two bearing parts do not come directly into touching contact with each other. As a result, the wear of the bearing is greatly reduced compared to bearings in which solid friction occurs, or mixed friction.
  • the overpressure required to implement the bearing function is able to be applied essentially by the two bearing parts themselves, if a sufficiently high rotational speed of the compressor runner or of the shaft is present. At a rotational speed below the minimum rotational speed required for building up the overpressure, a solid friction or a mixed friction takes place in the bearing. In this instance, the two bearing parts are directly in touching contact, which results in increased wear. In order to reduce this and to increase the service life of the bearing, costly materials are frequently used. In particular, when the drive assembly is designed for a start-stop operation, a considerable effort has to be made in order to achieve a sufficient service life of the bearing.
  • the fluid-dynamic bearing has to be constantly supplied, using the overpressure source, with fluid under pressure, gas in particular.
  • the overpressure source has to be constantly available, for instance, in the form of an external compressor. This, however, has a negative effect on costs as well as space requirement of the motor vehicle system device and particularly the charging device.
  • the compressor or a part of a tandem pump should be used as the overpressure source. It is self-explanatory that the tandem pump does not have to be present if the compressor is being used as the overpressure source. Besides the overpressure part used as the overpressure source, the tandem pump additionally has a low air pressure part, by the use of which it is also able to provide a low air pressure for the user of the motor vehicle system device and the motor vehicle. The user is accordingly a low air pressure user.
  • overpressure one should understand a pressure which is greater than a reference pressure. In contrast, the low air pressure is less than the reference pressure.
  • the reference pressure one may draw upon the environmental pressure, for example, or the atmospheric pressure.
  • Particular advantages with regard to space requirement come about by the use of the compressor or the tandem pump as the overpressure source for the bearing.
  • a cost reduction may be achieved by avoiding additional components, especially of the external overpressure source.
  • the bearing is a fluid-dynamic bearing
  • a sufficiently large overpressure may be generated in the bearing gap, using the overpressure source also below the minimum rotational speed, which enables operating the bearing only using fluid friction.
  • the overpressure provided by the overpressure source is clearly able to exceed the overpressure automatically generated by the two bearing parts, so that a greater bearing capability of the bearing is given.
  • Additional advantages are better cooling, because the bearing permanently has flowing through it fluid conveyed by the overpressure source. Accordingly, lower temperatures are present in the bearing. In this way, lower wear and thus a higher component part reliability are achieved.
  • One may also resort to more favorable materials or do without costly coatings, which enables a cost-effective production of the bearing, or the entire motor vehicle system device.
  • the bearing may also be reduced in size if the overpressure is large enough.
  • a cross sectional reduction device or a cross sectional adjusting device for setting the overpressure, produced in the bearing gap, be provided between the overpressure source and the bearing.
  • the overpressure source is able to produce an overpressure which is clearly greater than the overpressure required before the bearing gap, particularly because the bearing pressure built up by itself is still enough at higher rotational speeds.
  • the cross sectional reduction device or the cross sectional adjustment device is provided.
  • the cross sectional reduction device may be a throttle, for instance, or a restrictor that is not adjustable, that is, it has the effect of a constant cross sectional reduction in the flow connection between the overpressure source and the bearing.
  • the cross sectional adjustment device makes a controlled and/or regulated setting of the overpressure present in the bearing gap possible.
  • the cross sectional adjustment device is present as a valve, for example.
  • a simple closing/opening valve may be used in this case, for example.
  • the charging device may thus have the turbine, to which exhaust gas, particularly exhaust gas of the drive assembly, is able to be supplied.
  • the turbine is present as an exhaust gas turbine.
  • the turbine, or rather a turbine runner of the turbine, is operatively connected to the compressor or its compressor runner in such a way that the compressor is able to be driven using the exhaust gas flowing through the turbine.
  • the charging device is developed as an exhaust gas turbocharger device.
  • the drive of the compressor is implemented by the flow energy taken from the exhaust gas using the turbine.
  • the operative connection between the turbine, or rather its turbine runner, and the compressor, or rather its compressor runner, is usually implemented using a shaft, which is accommodated, at least in regions, in a rump housing, the shaft being operatively connected both to the turbine, or rather the turbine runner and the compressor, or rather the compressor runner, particularly connected in a torsionally rigid manner.
  • the drive of the compressor may be implemented using a drive device, particularly an electric motor.
  • a drive device particularly an electric motor.
  • the drive device is operatively connected to the shaft for the at least occasional driving of the compressor.
  • the drive device is also operatively connected to the shaft, or at least able to be operatively connected.
  • the drive device supports the turbine at least from time to time in driving the compressor.
  • the drive device and the turbine in common provide the torque required to drive the compressor.
  • the shaft described above is used particularly to support the compressor runner of the compressor, to which it is assigned.
  • the supporting of the turbine runner of the turbine may also be implemented using the shaft or the drive device, especially the electric motor. This support is attained with the aid of the bearing, which is accordingly developed as a shaft bearing.
  • the drive assembly is a fuel cell assembly having at least one fuel cell and at least one electric machine fed with electrical energy by the fuel cell.
  • Fuel cells frequently require an air supply device in order to supply it with an oxygenator, such as oxygen or environmental air, for the energy carrier, for example, hydrogen.
  • the compressor is used as air supply device, and the former, as has already been described, is able to be driven by the turbine and/or the electric drive device.
  • the air supply device one may use, for example, a displacement machine, such as a Roots blower or a rotary screw compressor.
  • turbo machines that is, turbochargers having a compressor and a turbine
  • the drive assembly may, of course, also be developed as an internal combustion engine, or have one.
  • the tandem pump be driven electrically. If the motor vehicle system device has an internal combustion engine, the low air pressure may be provided for its user, particularly at an intake manifold of the internal combustion engine. If, on the other hand, the drive assembly is a fuel cell assembly, this possibility drops out. The low air pressure must therefore be provided for the user in a different manner, for example, using an electrically driven pump. Thus, both for supplying the low air pressure to the user and also for supplying the overpressure to the bearing, a pump is required, in each case. However, installing two pumps is cost-connected for one thing, and for another, it increases the installation space required. For this reason, the tandem pump is used, using which both the overpressure and the low air pressure are able to be generated and provided. The tandem pump is provided with an electric drive, in this context.
  • the bearing be designed as an aerodynamic or an aerostatic sliding bearing.
  • the bearing is usually developed as a sliding bearing, the sliding bearing being able to be designed either for aerodynamic (fluid-dynamic) or aerostatic (fluid-static) operation.
  • the bearing be an axial bearing and/or a radial bearing.
  • a plurality of bearings may, of course, also be provided, in which case at least one axial bearing and/or at least one radial bearing is present. It may particularly be provided that there are two radial bearing and one axial bearing, the electric drive device being situated between the two radial bearings on the shaft that is operatively connected to the compressor runner.
  • the radial bearing on the other hand, is present between the compressor runner and the radial bearing facing the compressor runner. In this way, the shaft, or rather the compressor runner is fixed both in the radial direction and in the axial direction. If the bearing is used at the same time as axial bearing and as radial bearing, it may be designated as a combination bearing.
  • the user be a brake booster.
  • the motor vehicle system device additionally has the brake booster, which is connected to the tandem pump in a flow technological manner.
  • the tandem is able to provide to the brake booster the low air pressure (mostly pneumatic).
  • the present invention naturally also relates to a motor vehicle having a motor vehicle system device according to the statements above.
  • the present invention also relates to a method for operating a motor vehicle system device, particularly according to the above statements, the motor vehicle system device being equipped with a drive assembly to which a charging device is assigned which has a compressor having at least one compressor runner that is supported using at least one bearing, the bearing having a stationary first bearing part and a second bearing part that is operatively connected to the compressor runner.
  • a charging device is assigned which has a compressor having at least one compressor runner that is supported using at least one bearing, the bearing having a stationary first bearing part and a second bearing part that is operatively connected to the compressor runner.
  • an overpressure source be connected to the bearing, using which an overpressure is produced in a bearing gap present between the first bearing part and the second bearing part in at least one operating state of the charging device, the overpressure source being the compressor and/or a part of a tandem pump which, besides the overpressure, also provides low air pressure for a user provided in the motor vehicle.
  • the motor vehicle system device may be further refined according to the above statements.
  • the overpressure source During operation, especially when using a fluid-dynamic sliding bearing as the bearing, it is not necessary for the overpressure source to make available permanent overpressure to the bearing. Rather, at a rotational speed of the compressor runner, or of the shaft operatively connected to it, an automatic buildup of the overpressure in the bearing gap may occur, conditioned by the relative motion between the first bearing part and the second bearing part. That is, the overpressure does not have to be made available permanently by the overpressure source. Equally well this may be provided in order, for instance, to increase the overpressure present in the bearing gap and correspondingly to improve the bearing capability of the bearing. Whether the bearing is supplied with overpressure using the overpressure source depends on the instantaneous operating state of the charging device. Thus it may be provided that, in the at least one operating state, the overpressure present in the bearing gap is produced using the overpressure source. In another operating state, however, this is not the case.
  • One refinement of the present invention provides that, only in an operating state in which the rotational speed of the compressor is less than a certain minimum rotational speed, the (sufficiently large) overpressure between the bearing parts be produced using the overpressure source.
  • the overpressure is able to build up in the bearing automatically if the rotational speed of the compressor runner is greater than or equal to the certain minimum rotational speed. This is particularly the case if the bearing is developed as a fluid-dynamic sliding bearing.
  • the minimum rotational speed is undershot by the rotational speed, should the (sufficiently great) overpressure between the bearing parts, or rather, in the bearing gap be produced using the overpressure source. In other operating states this is not necessary.
  • a bearing developed as a fluid-static bearing on the other hand, it is usual to supply overpressure to it always using the overpressure source.
  • FIGURE shows a schematic representation of a motor vehicle system device.
  • the FIGURE shows a motor vehicle system device 1 having a drive assembly 2 , to which a charging device 3 is assigned.
  • Charging device 3 has at least one compressor 4 to which a shaft 5 is assigned for supporting a compressor runner (not shown here in detail) of compressor 4 .
  • Compressor 4 is used for compressing fluid, particularly gas, for instance air, which is able to be supplied to it by a compressor inlet 6 .
  • Compressor 4 makes available the compressed fluid at a compressor outlet 7 .
  • the compressed fluid is supplied to drive assembly 2 , for example.
  • Drive assembly 2 is, for instance, a fuel cell assembly having at least one fuel cell 8 and an electric machine not shown here, which is supplied with electric current by fuel cell 8 .
  • an internal combustion engine may be provided, of course.
  • charging device 3 is developed as an exhaust gas turbocharger device. This means that, besides compressor 4 , it has a turbine 9 . Exhaust gas, particularly of drive assembly 2 , is able to be supplied to turbine 9 via a turbine inlet 10 . In turbine 9 , the exhaust gas supplied via turbine inlet 10 flows through a turbine runner, not shown here, which is also supported using shaft 5 . After that, the exhaust gas flows out of turbine 9 from a turbine outlet 11 , for instance, into the exhaust gas tract, not shown here, of drive assembly 2 or motor vehicle system device 1 .
  • Both the compressor runner and the turbine runner are connected to shaft 5 in a torsionally rigid manner. Accordingly, there is an operative connection between compressor 4 and turbine 9 via shaft 5 . Consequently, compressor 4 is able to be driven using turbine 9 if the exhaust gas is supplied to it.
  • Shaft 5 is situated in a rump housing 12 , at least in sections. Rump housing 12 is usually situated between compressor 4 and turbine 9 , in this instance. In this way, the heating up of the fluid supplied to compressor 4 by the heat of the exhaust gas supplied to turbine 9 is at least reduced. However, this also means that rump housing 12 is able to be acted upon by just this heat, and heated up by it.
  • Bearings 13 , 14 and 15 are situated in rump housing 12 , which are used to support shaft 5 .
  • bearings 13 to 15 are developed as shaft bearings.
  • Bearings 13 and 14 are used as radial bearings, that is, they are only able to take up forces in the radial direction, but not in the axial direction.
  • Bearing 15 is developed as an axial bearing, and thus it prevents an axial shift of shaft 5 , but it cannot take up any radial forces. It is obvious that such an exemplary embodiment of bearing 13 to 15 is purely exemplary. Of course, each bearing 13 to 15 may be designed axial, radial or axial and radial forces.
  • rump housing 12 accommodates a drive device 16 which is designed as an electric motor, for example.
  • Drive device 16 is operatively connected or able to be operatively connected to shaft 5 .
  • the former is provided particularly in operating points of drive assembly 2 , in which no sufficiently large quantity of exhaust gas is generated to operate turbine 9 .
  • motor vehicle system device 1 has a fluid inlet 17 , to which compressor 4 or compressor inlet 6 is connected via an intake line 18 .
  • fluid intake 17 has a filter (not shown here).
  • Bearings 13 , 14 and 15 each have a first bearing part 19 and a second bearing part 20 , the first bearing part 19 being always situated in a stationary manner, and second bearing part 20 being assigned to the compressor runner of compressor 4 and connected to the latter in a torsionally rigid manner. Accordingly, a rotation of the compressor runner also effects a rotation a rotation of second bearing parts 20 of bearings 13 , 14 and 15 .
  • First bearing parts 19 may, in particular, be bearing bushes of bearings 13 , 14 and 15
  • second bearing parts 20 at least in the case of radial bearings 13 and 14 may be formed by a region of shaft 5 .
  • second bearing part 20 may be a radial projection extending outwards from shaft 5 in the radial direction, which cooperates with first bearing part 19 for the axial fixing of shaft 5 .
  • bearing gap 21 Between bearing parts 19 and 20 there is in each case a bearing gap 21 .
  • a certain overpressure of the fluid, especially air, located in this bearing gap 21 has to be present. Otherwise, the two bearing parts 19 and 20 will come into touching contact with each other, so that mixed friction or even solid friction among each other will take place. In particular, based on the additional thermal stress, this may lead to a shortening of the service lives of bearings 13 to 15 .
  • bearings 13 to 15 are developed as fluid-dynamic bearings, the sufficiently great overpressure will take place automatically upon the achieving or exceeding of a minimum rotational speed by the rotational speed of shaft 5 . This is the case, based on the pumping effect of the two bearing parts 19 and 20 . They form a wedge, particularly when loaded, into which the fluid is transported. In this context, the pressure, under which the fluid is present, is increased, so that the overpressure is produced.
  • one part of bearings 13 to 15 is able to be developed as a fluid-dynamic bearing and the other part as a fluid-static bearing. Also, one part of bearings 13 to 15 may be present as a roller bearing.
  • a (first) overpressure source 22 is connected to bearings 13 to 15 , which sucks fluid from fluid intake 17 via a suction line 23 , compresses it and supplies it to bearings 13 to 15 via a connecting line 24 .
  • a cross sectional reduction device 25 or, as shown here, a cross sectional adjustment device 25 may be provided.
  • overpressure line 27 is connected which, on its other side has a flow connection to compressor outlet 7 .
  • overpressure line 27 there is also provided a cross sectional adjustment device 28 .
  • Compressor 4 may thus be used as a second overpressure source 22 ′.
  • the overpressure present in bearing gap 21 may thus be provided to bearings 13 to 15 , using overpressure source 22 and/or using second overpressure source 22 ′, that is, compressor 4 .
  • the overpressure is made available using overpressure sources 22 and 22 ′ in an operating state of charging device 3 , in which the exhaust gas conducted through turbine 9 is not sufficient for driving compressor 4 , or rather, for making available a sufficiently high overpressure at compressor outlet 7 .
  • the overpressure present at compressor outlet 7 is sufficient, however, in the case of a further operating state, the overpressure prevailing in bearing gap 21 is able to be produced exclusively using compressor 4 .
  • overpressure source 22 and/or overpressure source 22 ′ may be switched off or at least disconnected from the respective bearing 13 to 15 by interrupting the flow connection. At high rotational speeds, one may, under certain circumstances, do without the overpressure from compressor 4 and/or overpressure source 22 .
  • Motor vehicle system device 1 preferably has a user 29 , for whose operation low air pressure is required. Consequently, it is necessary to provide both a low air pressure source 30 for providing the low air pressure for operating user 29 and an overpressure source 22 .
  • Both overpressure source 22 and low air pressure source 30 are usually electrically operated pumps. For this reason, it is provided that both overpressure source 22 and low air pressure source 30 are part of a tandem pump 31 , using which both overpressure and low air pressure are able to be made available.
  • a low air pressure-providing part is designated as low pressure part, in this context, and an overpressure-providing part is designated as overpressure part 31 ′. In this context, only one electrical drive is required for tandem pump 31 .
  • tandem pump 31 which has only the one drive.
  • tandem pump 31 it is possible to provide both user 29 with low air pressure, from low air pressure source 30 , and bearings 13 to 15 with overpressure from overpressure source 22 . In accordance with this, savings in installation space and weight are achieved. Costs are also able to be lowered in this way.
  • rump housing 12 have one or more inlets 32 , through which fluid is able to get into an inner space of rump housing 12 .
  • bearings 13 to 15 , drive device 16 and shaft 5 are situated at least in regions.
  • At least one of inlets 32 in this context, is able to be connected to connecting line 24 or distributor 26 and at least one additional one of inlets 32 is able to be connected to overpressure line 27 .
  • First inlet 32 is thus connected, in a flow-technological manner, to overpressure source 22 and second inlet 32 is connected to compressor 4 , or rather its compressor outlet 7 . Accordingly, fluid under overpressure is able to be brought into inner space 33 .
  • Rump housing 12 has furthermore at least one outlet 34 , one of the outlets 34 shown here being connected in a flow-technological manner to a surroundings of motor vehicle system device 1 and the other of outlets 34 to an additional compressor inlet 35 .
  • Shown cross sectional adjustment devices are not able to be assigned to outlets 34 , using which the fluid mass flow, which gets out of rump housing 12 through outlets 34 is able to be set controllably and/or regulatedly or switchably. In this way, the pressure present in inner space 33 , that is, the low air pressure or the overpressure, are able to be set.
  • the cross sectional adjustment elements one may, of course, also use cross sectional reducing elements.
  • fluid is sucked in via fluid inlet 17 using compressor 4 or overpressure source 22 .
  • At least a part of the sucked up fluid is taken from rump housing 12 or its inner space 33 , in this context.
  • a fluid mass flow is created in rump housing 12 , particularly starting from at least one inlet 32 up to the at least one outlet 34 .
  • This fluid mass flow is preferably directed at thermally particularly highly stressed regions of rump housing 12 or elements situated in it, for instance, bearings 13 to 15 or drive device 16 . In this way, reliable cooling of these elements or regions is assured.
  • the fluid mass flow also takes care that moisture, particularly condensate, is sucked out of rump housing 12 .
  • corrosion within rump housing 12 is additionally avoided.
  • tandem pump 31 the required installation space and the costs of motor vehicle system device 1 are reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
US13/688,343 2011-12-01 2012-11-29 Method and system to reduce to wear on a bearing Active 2033-08-15 US10428826B2 (en)

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DE102011087606.5 2011-12-01
DE102011087606A DE102011087606A1 (de) 2011-12-01 2011-12-01 Kraftfahrzeugsystemeinrichtung sowie Verfahren zum Betreiben einer Kraftfahrzeugsystemeinrichtung
DE102011087606 2011-12-01

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US11428160B2 (en) 2020-12-31 2022-08-30 General Electric Company Gas turbine engine with interdigitated turbine and gear assembly

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180340470A1 (en) * 2017-05-25 2018-11-29 General Electric Company Method and structure of interdigitated turbine engine thermal management
US10787931B2 (en) * 2017-05-25 2020-09-29 General Electric Company Method and structure of interdigitated turbine engine thermal management
US11300051B2 (en) * 2019-02-01 2022-04-12 Honeywell International Inc. Engine systems with load compressor that provides cooling air
US11428160B2 (en) 2020-12-31 2022-08-30 General Electric Company Gas turbine engine with interdigitated turbine and gear assembly

Also Published As

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EP2600007A3 (fr) 2017-11-01
US20130142671A1 (en) 2013-06-06
EP2600007A2 (fr) 2013-06-05
DE102011087606A1 (de) 2013-06-06
EP2600007B1 (fr) 2019-05-15

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